CN106499814A - Hydraulic control system for the multi-mode electro-mechanical drive unit of automatic transmission - Google Patents

Hydraulic control system for the multi-mode electro-mechanical drive unit of automatic transmission Download PDF

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Publication number
CN106499814A
CN106499814A CN201610729192.9A CN201610729192A CN106499814A CN 106499814 A CN106499814 A CN 106499814A CN 201610729192 A CN201610729192 A CN 201610729192A CN 106499814 A CN106499814 A CN 106499814A
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CN
China
Prior art keywords
electromagnetic valve
valve
hydraulic
clutch
control system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201610729192.9A
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Chinese (zh)
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CN106499814B (en
Inventor
M·R·柯诺斯
M·D·福斯特
E·S·泰伦
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GM Global Technology Operations LLC
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GM Global Technology Operations LLC
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Publication of CN106499814A publication Critical patent/CN106499814A/en
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Publication of CN106499814B publication Critical patent/CN106499814B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • F16H61/0267—Layout of hydraulic control circuits, e.g. arrangement of valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
    • B60W10/11—Stepped gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W20/00—Control systems specially adapted for hybrid vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W20/00—Control systems specially adapted for hybrid vehicles
    • B60W20/10—Controlling the power contribution of each of the prime movers to meet required power demand
    • B60W20/15—Control strategies specially adapted for achieving a particular effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
    • F16H61/686—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with orbital gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units, or advanced driver assistance systems for ensuring comfort, stability and safety or drive control systems for propelling or retarding the vehicle
    • B60W30/18—Propelling the vehicle
    • B60W30/184—Preventing damage resulting from overload or excessive wear of the driveline
    • B60W30/1843—Overheating of driveline components
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/90—Vehicles comprising electric prime movers
    • B60Y2200/92—Hybrid vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2300/00—Purposes or special features of road vehicle drive control systems
    • B60Y2300/18—Propelling the vehicle
    • B60Y2300/182—Selecting between different operative modes, e.g. comfort and performance modes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2300/00—Purposes or special features of road vehicle drive control systems
    • B60Y2300/42—Control of clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/42—Clutches or brakes
    • B60Y2400/424—Friction clutches
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S903/00—Hybrid electric vehicles, HEVS
    • Y10S903/902—Prime movers comprising electrical and internal combustion motors
    • Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
    • Y10S903/904—Component specially adapted for hev
    • Y10S903/912—Drive line clutch
    • Y10S903/914—Actuated, e.g. engaged or disengaged by electrical, hydraulic or mechanical means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S903/00—Hybrid electric vehicles, HEVS
    • Y10S903/902—Prime movers comprising electrical and internal combustion motors
    • Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
    • Y10S903/904—Component specially adapted for hev
    • Y10S903/915—Specific drive or transmission adapted for hev
    • Y10S903/917—Specific drive or transmission adapted for hev with transmission for changing gear ratio

Abstract

A kind of hydraulic control system for motor vehicles multi-mode electro-mechanical drive unit includes multiple torque-transmitting mechanisms, and each torque-transmitting mechanisms includes at least one friction clutch.Multiple clutch control valves respectively with torque-transmitting mechanisms in a fluid communication, and operable so that the state of torque-transmitting mechanisms is changed over clutched state from clutch off-state when activateding.Electromagnetic valve is matched and is in fluid communication with the clutch control valve respectively.Normally opened force-variable electromagnetic valve is in fluid communication with electromagnetic valve.The hydraulic pressure between electromagnetic valve and its clutch control valve of pairing under any open mode of the operation setting of normally opened force-variable electromagnetic valve.

Description

Hydraulic control system for the multi-mode electro-mechanical drive unit of automatic transmission
Technical field
The present invention relates to for the hydraulic control system of automatic transmission, and more particularly relate to mix fluid drive The hydraulic control system of device, the mixing automatic transmission have the hydraulic operated clutch selected for scope.
Background technology
Typical automatic transmission includes hydraulic control system, its be used with to the part in variator provide cooling and Lubrication, and activate multiple torque transmitters to be allowed for the synchronization that shift gears between multiple gear ratio that variator is exported.This A little torque transmitters can be, for example, the friction clutch that arranges together with gear train or arrange in torque-converters and braking Device.Traditional hydraulic control system generally comprises main pump, and the main pump provides pressurized stream to the solenoid in multiple valves and valve body Body, such as oil.Via multiple valves and multiple electromagnetic valves for being individually controlled each clutch control valve, pressurized hydraulic fluid is led Draw by hydraulic fluid circuit controlling to shift gears via torque transmitter.Pressurized hydraulic fluid is also led to various subsystems System, which includes lubrication subsystem, cooling subsystem and converter clutch control subsystem.It is transported to adding for shift actuator Hydraulic fluid under pressure is used for out of engagement with torque transmitter obtaining different gear ratios.
Known automatic transmission is generally made in multiple mode of operation, and the operator scheme includes not parking driving mould Formula and parking mode.Do not park drive pattern and generally include forward gear or speed ratio (i.e. drive pattern), at least one reverses gear Gear or speed ratio (i.e. reverse mode) and neutral mode.General by engage gear level or other driver interface devices come The selection of various drive patterns is completed, the gear level or other driver interface devices are connected by gearshift cable or other machineries Fitting is connected to variator.Or, (ETRS) system (also referred to as " line traffic control gearshift " system can be selected by electronic transmission scope System) control drive pattern selection.In ETRS system, by the e-mail transmitted between driver interface device and variator Number complete the selection of drive pattern.
Although aforementioned control system of speed variator is useful for its expected purpose, remain a need in variator new and Improved hybrid transmission hydraulic control system configuration, its reduce the quantity of control valve and simplify the control of clutch control System, during being included in variator default conditions.Default conditions are that variator is experienced without electronically controlled hydraulic state.Acquiescence Variator no longer has the ability that desired gear condition realized by electronically order solenoid.Default conditions intentionally can be ordered (for example when diagnosis shows that the solenoid driver for damaging, the controller for damaging, controller are shut down at high temperature) or can be due to hard Part failure and by mistake there is (such as controller failure, wire harness failure, solenoid driver failure).Accordingly, it would be desirable to a kind of use In the improved hydraulic control system that hydraulic hybrid activates automatic transmission, the complexity of electromagnetic valve is which reduced and in acquiescence shape Different driving conditions can be provided under state.
Content of the invention
Provide a kind of hydraulic control system for hybrid transmission.Hydraulic control system provides three (3) individual fixations Gear ratio and four (4) plant EV patterns, and variator loses electronically controlled multiple acquiescence shapes wherein when in drive pattern State.Hydraulic control system includes that six (6) individual often low on-off solenoids, one (1) individual often high variable force solenoid, one (1) individual are used for The regulating valve of line pressure control, and six (6) the individual on-off guiding valves controlled for clutch actuation and motor cooling.Additionally, Other passive devices also multiple, such as one (1) individual accumulator, two (2) individual pressure relief valves, one (1) individual feeding limit valve, with And one (1) individual bypass valve.
Hydraulic control system for the multi-mode electro-mechanical drive unit of motor vehicles includes multiple torque-transmitting mechanisms, per Individual torque-transmitting mechanisms include at least one friction clutch.Multiple clutch control valves respectively with torque-transmitting mechanisms in one Individual fluid communication, and when activated operable with by the state of torque-transmitting mechanisms from clutch off-state change over from Clutch engagement state.Electromagnetic valve is matched and is in fluid communication with clutch control valve respectively.Normally opened force-variable electromagnetic valve It is in fluid communication with line pressure control and regulation valve.The operation setting of the force-variable electromagnetic valve hydraulic pressure of system, and activate Device feeding limits valve and limits the maximum pressure between electromagnetic valve and its clutch control valve of pairing under any one open mode Power.
In an example of the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention, Main supply line includes hydraulic fluid, and which makes each torque-transmitting mechanisms be connected to main supply after clutch control valve activated Pipeline.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, hydraulic fluid in the pump operated main supply line with movement simultaneously pressurizes to which.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, pump is fixed displacement pump.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, there is provided each in assembled hydraulic collector, wherein electromagnetic valve and force-variable electromagnetic valve is connected with assembled hydraulic collection pipe fluid Logical, and the operation of force-variable electromagnetic valve is used for the hydraulic pressure that arranges the hydraulic fluid in assembled hydraulic collector.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, multiple torque-transmitting mechanisms include four torque-transmitting mechanisms for limiting drive mechanism for vehicle, and limit brake coupling The 5th torque-transmitting mechanisms.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, transmission control module is connected to and orders the operation of each electromagnetic valve and force-variable electromagnetic valve.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, electromagnetic valve includes first, second, third, fourth and fifth electromagnetic valve, by transmission control module and the clutch control of pairing Valve processed orders any one in the first, second, third, fourth of opening or the 5th electromagnetic valve to be all exposed to identical hydraulic pressure together Under Fluid pressure, feed till limiting the restriction that valve is arranged until actuator.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, multiple electromagnetic valves can respectively the off status for making closed electromagnetic valve and make electromagnetic valve open open state in a kind of state Lower operation.
Another example in the hydraulic control system of the multi-mode electro-mechanical drive unit for motor vehicles of the present invention In, wherein in electromagnetic valve, predetermined several electromagnetic valves are provided as the force-variable electromagnetic valve provided under normally open, electromagnetism In valve, predetermined several electromagnetic valves are during the default conditions of the hydraulic control system of operational control of electromagnetic valve are lost, it is allowed to flow Body connection is under clutched state with being kept for two in clutch control valve.
By reference to following description and accompanying drawing, other features of the present invention, aspect and advantage will become clear from, In accompanying drawing, same reference represents identical part, element or feature.
Description of the drawings
Accompanying drawing described herein merely for the purpose of illustration and is not intended to be limiting in any manner the scope of the present invention.
Fig. 1 is the top view of the exemplary power power train of the present invention in motor vehicles；
Fig. 2A-Fig. 2 B provide the diagram of a part for the hydraulic control system of the principle according to the present invention；
Fig. 3 A- Fig. 3 B provide a part for the hydraulic control system that is changed by the hydraulic control system of Fig. 2A-Fig. 2 B Diagram；And
Fig. 4 A- Fig. 4 B provide a part for the hydraulic control system that is changed by the hydraulic control system of Fig. 3 A- Fig. 3 B Diagram.
Specific embodiment
With reference to Fig. 1, show motor vehicles and generally represented by reference 2.Motor vehicles 2 are illustrated as car, It should be understood that motor vehicles 2 can be any kind of vehicle, and such as, truck, van, SUV etc..Machine Motor-car 2 includes exemplary power power train 10.Although first it should be understood that having illustrated rear wheel drive PWTN, In the case of without departing substantially from the scope of the present invention, motor vehicles 2 can have front-wheel drive PWTN.PWTN 10 Generally include and mix the electromotor 12 that automatic transmission 14 is connected with each other.
In the case of without departing substantially from the scope of the present invention, electromotor 12 can be traditional internal combustion engine or motor Prime mover of machine, hybrid engine or any other type.Electromotor 12 by flex plate 16 or is connected to starter 18 other attachment means supply driving torque to variator 14.Starter 18 can be fluid power plant, such as, stream Body shaft coupling or torque-converters, wet-type dual-clutch, the dry type torsional damper or motor with spring.It should be understood that Can be using any starter for including dry launch clutch between electromotor 12 and variator 14.
There is variator 14 typical casting metals housing 20, the metal shell 20 to surround and protect each of variator 14 Individual part.Housing 20 includes that multiple holes, passage, shoulder and flange, the plurality of hole, passage, shoulder and flange are positioned and supported These parts.In general, variator 14 includes transmission input shaft 22 and transmission output shaft 24.Transmission input shaft 22 with Gear and clutch apparatus 26 are provided between transmission output shaft 24.Transmission input shaft 22 is via starter 18 in function Upper and electromotor 12 is connected with each other and from 12 receives input moment of torsion of electromotor or power.Therefore, transmission input shaft 22 can To be turbine wheel shaft in the case where starter 18 is as fluid power plant, in the case where starter 18 is as double clutch be Dual input shaft, or be drive shaft in the case where starter 18 is motor.Transmission input shaft 22 be attached to gear and Clutch apparatus 26 and driving torque is provided to the gear and clutch apparatus 26.For shown exemplary rear wheel drive car , transmission output shaft 24 is coupled with final driver element 28, and the final driver element 28 includes：For example, power transmission shaft 30, differential Device assembly 32 and the drive axle 34 for being connected to wheel 36.
Gear and clutch apparatus 26 include the first traction motor and the second traction motor, such as, limit electromechanical driving First motor-generator 38 and the second motor-generator 40 of unit, the electro-mechanical drive unit include：Limit Multiple gear trains of geared system 42, five (5) torque-transmitting mechanisms schematically shown by reference letter A-E and multiple Axle.Gear train can include single mesh gear, and such as one or more planetary gearsets, its pass through optionally to activate Multiple clutch/brakes and be connected to or may be selectively coupled to multiple axles.Multiple axles can include：Countershaft is right Axle, sleeve and central shaft, reverse gear or idling axle or its combine.By optionally by single gear connection in gear train To transmission output shaft 24, torque-transmitting mechanisms A-E optionally either alone or in combination engagement so as to initiate such as down to Few one：3 fixed gears or speed ratio, 4 electrically variable (EV) patterns and a reverse gear or speed ratio.A side In face, each torque-transmitting mechanisms A-D includes at least one friction clutch, and includes being respectively designated as according to many aspects Multiple friction clutches of A-1, B-1, C-1, D-1, and torque-transmitting mechanisms E includes friction clutch E-1, the friction clutch E-1 can serve as friction brake B1.It should be understood that the gear in the case of without departing substantially from the scope of the present invention, in variator 14 The concrete arrangement and number of group and axle can change.
Motor vehicles 2 include transmission control module 50.Transmission control module 50 is preferably non-universal electronics control Device processed, which has：The digital computer or processor of pre-programmed, control logic or circuit, for storing depositing for data Reservoir and at least one I/O ancillary equipment.Control logic include or allow multiple logic routines to monitor, to manipulate and Generate data and control signal.
The hydraulic control system 100 for being connected to transmission control module 50 and being controlled by transmission control module 50 is arranged on In valve body 102, the valve body 102 includes via fluid path and valve opening and accommodates most of parts of hydraulic control system 100.This A little parts are included but is not limited to：Pressure-regulating valve, directional valve, solenoid etc., have been carried out in further detail to which referring to figs. 2 to Fig. 4 Ground diagram and description.Valve body 102 can be attached to the bottom of case of transmission 20 or in rear-wheel drive transmission in front-wheel Drive the front portion that case of transmission 20 is attached in variator.Hydraulic control system 100 is operable as：It is selectively engaged moment of torsion Clutch A-1, B-1, C-1, D-1, E-1 of transmission mechanism A-E, and by optionally under the pressure (pressure come From the pump of such as fixed displacement pump 106, or accumulator (not shown), or auxiliary electric pump (not shown)) food tray 104 pass Hydraulic fluid is sent, and cooling to be provided for variator 14 and is lubricated.Pump 106 can be by electromotor 12 or assisted engine or electricity Dynamic motor drives.
With reference to Fig. 2A to Fig. 2 B and refer again to Fig. 1, it is illustrated that a part for hydraulic control system 100.Hydraulic control System 100 generally includes the subsystem of multiple being connected with each other or hydraulic communication, and the plurality of being connected with each other or hydraulic pressure connects Logical subsystem includes：Subsystem is controlled for activating the solenoid of multiple switch (often low) electromagnetic valve and a force-variable electromagnetic valve System 108, and for operate multiple clutch control valve C1, C2, C3, C4, C5 and torque-transmitting mechanisms A-E clutch A-1, The pressure of B-1, C-1, D-1, E-1 is adjusted and clutch control subsystem 110.Can also optionally provide and become for providing electronics The electronic transmission scope of fast device control selects (ETRS) part.Hydraulic control system 100 can also include scheming not in the drawings Each other subsystem for showing or module, such as, are adjusted with pressure and the lubrication that connects of clutch control subsystem 110 respectively Subsystem and cooling subsystem.
Pressure is adjusted and clutch control subsystem 110 is operable as providing and adjusting in whole hydraulic control system 100 Pressurized hydraulic fluid, such as transmission oil.Pressure is adjusted and clutch control subsystem 100 extracts flow of pressurized from food tray 104 Body.Food tray 104 is to be preferably provided in the case or reservoir at the bottom of case of transmission 20, from all parts of variator Return and collect in the case or reservoir with the hydraulic fluid in region.Hydraulic fluid is promoted simultaneously via pump 106 from food tray 104 And which is transmitted in whole hydraulic control system 100.Pump 106 can be：For example, gear pump, sickle pump, drum pump or Any other just or fixed displacement pump.Hydraulic fluid from pump 106 is controlled by pressure-regulating valve 112.Pressure-regulating valve 112 Adjust the pressure of the hydraulic fluid from pump 106 and pressurized hydraulic fluid is fed to main supply line under line pressure 114.In the case of without departing substantially from the scope of the present invention, main supply line 114 can include other branch lines and feed other sons System.In the case of without departing substantially from the scope of the present disclosure, pressure regulation can also include various with clutch control subsystem 110 Other valves and electromagnetic valve.
Main supply line 114 to solenoid control subsystem 108, pressure adjust and clutch control subsystem 110 and (when it is present) ETRS subsystem part feeding hydraulic oil.Main supply line 114 is to clutch control valve C1, clutch control valve C2, clutch control valve C3, clutch control valve C4 and clutch control valve C5 feeding hydraulic line pressure.Hydraulic control system 100 control clutch control valve C1, C2, C3, C4, C5 to guide pressurized hydraulic oil either alone or in combination, so as to control The engagement and release of clutch A-1, B-1, C-1, D-1, E-1 of torque-transmitting mechanisms A-E.Pressure is adjusted and clutch control System 110 also includes：Pressure-regulating valve 112, the feeding of exhaust gas recirculation regulating valve 116, actuator limit valve 118, supercharging accumulator 120th, multiple clutches of motor cooling control valve 122, main supply line pressure relief valve 124 and torque-transmitting mechanisms A-E A-1, B-1, C-1, D-1, E-1 and clutch control valve C1 that each is associated with torque-transmitting mechanisms A-E, C2, C3, C4, C5, as will be described below.
When it is present, ETRS subsystem part generally includes ETRS valve component 111.ETRS valve component 111 is alternatively to add Be electronically entered (that is, drive, move backward, stopping or neutral gear) that scope for request is selected is converted to hydraulic pressure and machinery life by addition The part of the subsystem architecture of order.Hydraulic pressure order is using the line pressure adjusted from pressure with clutch control subsystem 110 Hydraulic fluid is supplying hydraulic fluid to the part serviced by ETRS valve component 111 via main supply line 114.Machinery order The operation for such as engaging and departing from stop mechanism (not shown) can be included, the mechanism can be limiting transmission output shaft 26 Rotation traditional stop mechanism or the vehicle movement arresting system of any other type.
Pressure adjusts PR valves 112 to be included such as the supercharging with the inner space for feeding back bag FP more than right side of observation in Fig. 2A Bag BP.Relatively low hydraulic pressure in the pressurization bag BP of the electromagnetic valve being connected in solenoid control subsystem 108 is connected to master Higher hydraulic pressure balance in the feedback bag FP of supply line 114.Pressure-regulating valve 112 is used for balanced hydraulic control system Hydraulic operating pressure in 100.
The anti-regulator valve 116 of filling of aerofluxuss is connected to anti-filling return line 125, and which is collected and transmits from clutch The hydraulic fluid leak of control valve C1, C2, C3, C4, C5 and any leakage from not operation part, and thus maintain hydraulic pressure Oil continuously flow to the stator and torque-transmitting mechanisms of the first motor-generator 38 and the second motor-generator 40 Clutch A-1, B-1, C-1, D-1, E-1 of A-E, thus by the first motor-generator 38 and the second electro-motor-generating Clutch A-1, B-1, C-1, D-1, E-1 lubrication of machine 40 and torque-transmitting mechanisms A-E and cooling.Aerofluxuss are counter to fill actuator Valve 116 also provides the gross pressure protection of anti-filling return line 125, and this can generally have the operating pressure of approximate 30kPa.Row The anti-regulator valve 116 of filling of gas will be opened to discharge the pressure for exceeding expectation threshold value in anti-filling return line 125, and this originally may be used The state of clutch A-1, B-1, C-1, D-1, E-1 of any torque-transmitting mechanisms A-E can be negatively affected.
Actuator feeding limits valve 118 and operates to limit the electromagnetic valve for being applied to solenoid control subsystem 108 most Big pressure.
120 standardization of supercharging accumulator or limit from below in greater detail solenoid control subsystem 108 can The system pressure vibration of the operation of force solenoid (VFS) valve 144, which is controlled by the signal from transmission control module 50. Supercharging accumulator 120 goes back the system pressure vibration of standardization or restriction owing to the operation generation of fixed displacement pump 106, described solid The reciprocating operation generation system pressure oscillation of constant flow pump 106.Supercharging accumulator 120 can be configured to (for example) cause its It is movable in the whole operation pressure limit of boost-up circuit 127.
Motor cooling control valve 122 is normally close valve, and which provides active cooling state with by through clutch when opening Normal or passive oil stream that is that the leakage of control valve C1, C2, C3, C4, C5 is provided and coming reflexive filling loop 125 is not enough to cold But the first motor-generator 38, the clutch A-1 of the second motor-generator 40 and/or torque-transmitting mechanisms A-E, Increase cooling hydraulic oil when B-1, C-1, D-1, E-1 to the first motor-generator 38 and the second motor-generator 40 Stator and torque-transmitting mechanisms A-E clutch A-1, B-1, C-1, D-1, E-1 flowing.Motor cooling control valve 122 First motor-generator 38, second motor-generator 40 and moment of torsion transmission machine is increased to when opening on one's own initiative The oil stream of clutch A-1, B-1, C-1, D-1, E-1 of structure A-E.Although the oil stream of this increase is favourable under some modes of operation , but which is only desired when needing and increasing hydraulic pressure cooling oil, this is because increased oil stream is in motor cooling control Valve 122 must be supplied by the additional oil from pump 106 when opening, and thus increase the energy requirement of system.
Pressure relief valve 124 is connected to main supply line 114.Pressure relief valve 124 prevents the pressure in main supply line 114 Power exceedes to be expected maximum or arranges point pressure.
The temperature of the 126 sensing system hydraulic oil of thermal bypass valve of the discharge port of PR valves 112 is fluidly coupled to, and is set It is set to and opens when the temperature of hydraulic oil exceedes predetermined temperature.Thermal bypass valve 126 is normally closed preventing hydraulic oil from flowing to hydraulic pressure Oil heat exchanger 128, thus allows hydraulic oil to heat during system start-up.Hydraulic oil is generally supplied via thermal bypass valve 126 Lubricating component to variator lubricating loop.When hydraulic fluid temperature reaches predetermined temperature, thermal bypass valve 126 is opened to allow liquid Force feed stream is by hydraulic oil heat-exchangers 128 with cooled before the lubricating component of variator lubricating loop is flow to.
Coolant relief valve 130 is connected to and hydraulic oil is fed in the pipeline of thermal bypass valve 126.If oil is fed to Any pipeline of variator lubricating loop becomes clogged up, then coolant relief valve 130 is opened.This guarantees always there is minimum lubrication Oil flow to variator lubricating loop, even if oil is higher than predetermined temperature (at a predetermined temperature, it usually needs using hydraulic oil heat exchange Device 128 is cooled down) it is also so.
Transmission control module 50 is connected to multiple often low (the closing or normally closed) electromagnetic valve of solenoid control subsystem 108 Each solenoid and order each solenoidal operation.Normal low (closing) electromagnetic valve of solenoid control subsystem 108 includes One electromagnetic valve 132, the second electromagnetic valve 134, the 3rd electromagnetic valve 136, the 4th electromagnetic valve 138, the 5th electromagnetic valve 140, which is each grasped Make ground to match and be in fluid communication with clutch control valve C1, C2, C3, C4, C5.6th electromagnetic valve 142 and motor Cooling control valve 122 is in fluid communication, and allows hydraulic fluid to flow through motor cooling control valve 122 when being powered and opening.According to many Individual aspect, solenoid control subsystem 108 also include only the single variable output electromagnetism for being provided as force-variable electromagnetic valve 144 Valve.The solenoid of force-variable electromagnetic valve 144 is often high so that force-variable electromagnetic valve 144 is normally opened.Transmission control module 50 operations for being additionally coupled to force-variable electromagnetic valve 144 and order force-variable electromagnetic valve 144.
The hydraulic control system 100 of the present invention is with the difference of known transmission control system：Which only provides use The single of any one in clutch control valve C1, C2, C3, C4, C5 or whole hydraulic fluid pressure is transported in control Variable delivery valve, force-variable electromagnetic valve 144.The solenoid of force-variable electromagnetic valve 144 is received from transmission control module 50 Operation signal, the transmission control module 50 are to be connected to PR valves 112 by hydraulic line 127 and also include supercharging accumulator 120.Force-variable electromagnetic valve 144 and pressure adjust PR valves 122 and supercharging accumulator 120 to be used for being set or changed being connected to together First electromagnetic valve 132, the second electromagnetic valve 134, the 3rd electromagnetic valve 136, the 4th electromagnetic valve 138, the 5th electromagnetic valve 140 and the 6th electricity Necessary operating pressure in the assembled hydraulic collector 146 of each in magnet valve 142.In assembled hydraulic collector 146, hydraulic oil can By being provided to the first electromagnetic valve 132, the second electromagnetic valve 134, the 136, the 4th electricity of the 3rd electromagnetic valve by transmission control module 50 The opening of any one or ON signal order in magnet valve 138, the 5th electromagnetic valve 140 or the 6th electromagnetic valve 142 and provide to clutch Any desired one or more combinations of any one in device control valve C1, C2, C3, C4, C5.It should be noted that systematic pipeline pressure The pressure in assembled hydraulic collector 146 can be exceeded.
By transmission control module 50 be designated as open the first electromagnetic valve 132, the second electromagnetic valve 134, the 3rd electromagnetic valve 136th, any one in the 4th electromagnetic valve 138, the 5th electromagnetic valve 140 or the 6th electromagnetic valve 142 is each exposed to assembled hydraulic collection Identical hydraulic fluid pressure present in pipe 146, therefore the first electromagnetic valve 132, the second electromagnetic valve 134, the 3rd electromagnetic valve 136, During 4th electromagnetic valve 138 or the 5th electromagnetic valve 140 will not be will differ from by other clutch control valves C1, C2, C3, C4, C5 Hydraulic pressure of any one reception be delivered to which matches or associated clutch control valve C1, C2, C3, C4, C5.
For example, if torque demand combine vehicle sensing mode of operation (for example, speed, acceleration/deceleration speed, plus Fast device pedal position etc.) need activate torque-transmitting mechanisms B and D clutch B1, D1, then transmission control module 50 is ordered Second electromagnetic valve 134 and the 4th electromagnetic valve 138 change into high (opening-valve opening) from often low (closing of pass-valve).Second electromagnetic valve 134 and the 4th electromagnetic valve 138 open and reposition clutch control valve C2 to guide the hydraulic oil in assembled hydraulic collector 146 With C4 engaging clutch B1, D1 of torque-transmitting mechanisms B and D.
First electromagnetic valve 132, the second electromagnetic valve 134, the 3rd electromagnetic valve 136, the 4th electromagnetic valve 138, the 5th electromagnetic valve 140 Solenoid with the 6th electromagnetic valve 142 is often low and is only positioned to low (closing) position or height (opening) position or valve open position Put.First electromagnetic valve 132, the second electromagnetic valve 134, the 3rd electromagnetic valve 136, the 4th electromagnetic valve 138, the 5th electromagnetic valve 140 and Six electromagnetic valves 142 do not have variable fan-out capability, and therefore cannot be used for changing to the clutch A-1 of torque-transmitting mechanisms A-E, The hydraulic pressure of B-1, C-1, D-1, E-1.According to many aspects, the only force-variable electromagnetic valve 144 of solenoid control subsystem 108 Can operate to change hydraulic pressure.Clutch control valve C1, C2, C3, C4, C5 can be therefore or in the first electromagnetic valves 132nd, when the second electromagnetic valve 134, the 3rd electromagnetic valve 136, the 4th electromagnetic valve 138 and/or the 5th electromagnetic valve 140 are closed with combine liquid Pressure collector 146 is isolated, or is exposed to whole hydraulic pressures of assembled hydraulic collector 146 when electromagnetic valve is opened.
The hydraulic control system 100 of the present invention recognizes which torque-transmitting mechanisms A-D needs maximum hydraulic pressure pressure to maintain Moment of torsion under mode of operation, and set or control the position of force-variable electromagnetic valve 144 to tie up the pressure in main supply line 114 Hold in the pressure.Remaining one other operations clutch A-1, B-1, C-1, D-1 of torque-transmitting mechanisms A-D will be therefore whole Control under the pressure higher than corresponding torque-transmitting mechanisms A-D demands to meet its operational order.This simplifies hydraulic control The part and mode of operation of system 100.
The actuating of the clutch A-1 of clutch control valve C1 control mode transmission mechanism A.Clutch control valve C1 includes many Individual port, the plurality of port include the port for being connected to main supply line 114.Clutch control valve C1 is by opening the first electromagnetism Valve 132 and away from close or disengaged position movement.As it was previously stated, the first electromagnetic valve 132 is chosen as often low (closing) electromagnetic valve, which is closing Or closed mode prevents the operation of the clutch A-1 of torque-transmitting mechanisms A.In disengaging configuration, the first electromagnetic valve 132 is closed, So as to the hydraulic pressure in assembled hydraulic collector 146 is isolated with the fluid feed circuit 148 for being connected to clutch control valve C1. In bonding station, the first electromagnetic valve 132 is to open, and which is via fluid feed circuit 148 by the liquid in assembled hydraulic collector 146 Pressure pressure is connected to the port in clutch control valve C1, and clutch control valve C1 and opens, so as to via clutch supply pipe Line 150 transmits hydraulic pressure frictionally to couple the clutch A-1 of torque-transmitting mechanisms A.Clutch control valve C1 can be further Including the valve that is slidably arranged in the hole being formed in valve body or guiding valve, the valve body is in disengaging configuration (being shown in Fig. 2A) and engagement May move between position (not shown) (wherein valve moves to right side).Trunk Line pressure circuit or Trunk Line 114 be eventually introduced from Clutch A-E." line pressure arbitration logic " is used to be also referred to as " principal pressure arbitration logic ", by transmission control module 50 come really Determine the pressure in Trunk Line pressure circuit.Supervisor's line pressure based on highest demand is adjusting variable force solenoid 114.
The actuating of the clutch B-1 of clutch control valve C2 control mode transmission mechanism B.Clutch control valve C2 includes many Individual port, the plurality of port include the port for being connected to main supply line 114.Clutch control valve C2 is by opening the second electromagnetism Valve 134 and away from close or disengaged position movement.As it was previously stated, the second electromagnetic valve 134 is selected as often low (closing) electromagnetic valve, its The operation of the clutch B-1 of torque-transmitting mechanisms B is prevented under pass or closed mode.In disengaging configuration, 134 quilt of the second electromagnetic valve Close, so as to by the hydraulic pressure in assembled hydraulic collector 146 and the fluid feed circuit 152 for being connected to clutch control valve C2 Isolation.In bonding station, the second electromagnetic valve 132 is to open, and which is via fluid feed circuit 152 by assembled hydraulic collector 146 In hydraulic pressure be connected to port in clutch control valve C2, and clutch control valve C2 and open, so as to via clutch Hydraulic pressure is sent to supply line 154 the clutch B-1 of torque-transmitting mechanisms B.Clutch control valve C2 further can be wrapped The valve or guiding valve being slidably arranged in the hole being formed in valve body is included, the valve body is in disengaging configuration (being shown in Fig. 2A) and engagement position Put.
The actuating of the clutch C-1 of clutch control valve C3 control mode transmission mechanism C.Clutch control valve C3 includes many Individual port, the plurality of port include the port for being connected to main supply line 114.Clutch control valve C3 is by opening the 3rd electromagnetism Valve 136 and away from close or disengaged position movement.As it was previously stated, the 3rd electromagnetic valve 136 is selected as often low (closing) electromagnetic valve, its The operation of the clutch C-1 of torque-transmitting mechanisms C is prevented in pass or closed mode.In disengaging configuration, the 3rd electromagnetic valve 136 is closed Close, so as to by the hydraulic pressure in assembled hydraulic collector 146 be connected to the fluid feed circuit 156 of clutch control valve C3 every From.In bonding station, the 3rd electromagnetic valve 136 is to open, and which is via fluid feed circuit 156 by assembled hydraulic collector 146 Hydraulic pressure be connected to port in clutch control valve C3, and clutch control valve C3 and open, so as to supply via clutch Answer pipeline 158 that hydraulic pressure is sent to the clutch C-1 of torque-transmitting mechanisms C.Clutch control valve C3 can be further included The valve being slidably arranged in the hole being formed in valve body or guiding valve, the valve body is in disengaging configuration (being shown in Fig. 2A) and bonding station May move between (not shown) (wherein valve moves to right side).
The actuating of the clutch D-1 of clutch control valve C4 control mode transmission mechanism D.Clutch control valve C4 includes many Individual port, the plurality of port include the port for being connected to main supply line 114.Clutch control valve C4 is by opening the 4th electromagnetism Valve 138 and away from close or disengaged position movement.As it was previously stated, the 4th electromagnetic valve 138 is selected as often low (closing) electromagnetic valve, its The operation of the clutch D-1 of torque-transmitting mechanisms D is prevented in pass or closed mode.In disengaging configuration, the 4th electromagnetic valve 138 is closed Close, so as to by the hydraulic pressure in assembled hydraulic collector 146 be connected to the fluid feed circuit 160 of clutch control valve C4 every From.In bonding station, the 4th electromagnetic valve 138 is to open, and which is via fluid feed circuit 160 by assembled hydraulic collector 146 Hydraulic pressure be connected to port in clutch control valve C4, and clutch control valve C4 and open, so as to supply via clutch Answer pipeline 162 that hydraulic pressure is sent to the clutch D-1 of torque-transmitting mechanisms D.Clutch control valve C4 can be further included The valve being slidably arranged in the hole being formed in valve body or guiding valve, the valve body is in disengaging configuration (being shown in Fig. 2A) and bonding station May move between (not shown) (wherein valve moves to right side).
The actuating of the clutch E-1 of clutch control valve C5 control mode transmission mechanism E, which can serve as mentioned before For the brake coupling for keeping electromotor 12 stable.Clutch control valve C5 includes that multiple ports, the plurality of port include connecting It is connected to the port of main supply line 114.Clutch control valve C5 is by the 5th electromagnetic valve 140 of opening away from pass or disengaged position Mobile.As it was previously stated, the 5th electromagnetic valve 140 is selected as often low (closing) electromagnetic valve, which prevents moment of torsion from passing in pass or closed mode Pass the operation of the clutch E-1 of mechanism E.In disengaging configuration, the 5th electromagnetic valve 140 is closed, so as to by assembled hydraulic collector 146 In hydraulic pressure isolate with the fluid feed circuit 164 for being connected to clutch control valve C5.In bonding station, the 5th electromagnetic valve 140 is to open, and the hydraulic pressure in assembled hydraulic collector 146 is connected to clutch control via fluid feed circuit 164 by which Valve C5 processed, and the port opening in clutch control valve C5, so as to be sent to hydraulic pressure via clutch supply line 166 The clutch E-1 of torque-transmitting mechanisms E.
With continued reference to Fig. 1 and Fig. 2A-Fig. 2 B, actuator feeding limits valve 118 and is connected to combination liquid via shared pipeline 168 Pressure collector 146, actuator feeding limit valve 118 and are connected to main supply line 114 by feeding supply on restriction pipeline 170.Motor Cooling valve 122 cools down valve fluid feed circuit 172 by motor and is connected to the 6th electromagnetic valve 142, and cools down valve by motor Connecting pipeline 174 is connected to pressure and adjusts PR valves 112.Pressure is adjusted PR valves 112 and is connected by heat exchanger connecting pipeline 176 Connect, the outlet of hot bypass valve 126 is connected to transmission lubricating system by transfer line 178.
Hydraulic control system 100 is operable with three optional forward gears of offer and four EV patterns.In drive During variator default conditions during dynamic operator scheme, there is provided several optional default mode of operation.Experience in variator 14 During without electronically controlled default conditions, variator 14 is no longer able to the helical of tele command solenoid control subsystem 108 Pipe is obtaining desired gear condition., although VFS electromagnetic valves 144 are remained on, but first, second, third, therefore 4th, the 5th and the 6th electromagnetic valve 132,134,136,138,140 is maintained at inactive state, and corresponding clutch control valve C1, C2, C3, C4, C5 are in disengaging configuration.Meanwhile, adjust from pressure and clutch control subsystem 110 is supplied to main supply pipe The pressure of the regulation of line 114 is defaulted as limiting valve 118 by feeding and pressure adjusts the pressure limited by the design of PR valves 112.? Defined in Fig. 2A -2B during the default conditions of system, the clutch of variator 12 is defaulted as in neutral gear (disengaged) position.
With reference to Fig. 3 A- Fig. 3 B and Fig. 2A-Fig. 2 B are referred again to, hydraulic control system 200 is changed by hydraulic control system 100 Get, which passes through to change the part of solenoid control subsystem 108 to create solenoid control subsystem 202.For solenoid For control subsystem 202, solenoid control subsystem 108 second and the 4th electromagnetic valve 134,138 respectively by normal height (opening) Variable output solenoid valve 204,206 is substituted.Because force-variable electromagnetic valve 144 is retained, so as to providing Chang Gao or opening valve shape State, the available hydraulic in assembled hydraulic collector 146 still can use.Hydraulic pressure can be via 204,206 points of normally opened variable output solenoid valve Stream, signals to solenoid to change the pressure output of variable output solenoid valve 204,206 without the need for generally available Electronic Control. Due to the availability of normally opened variable output solenoid valve 204,206, clutch control valve C2 and C4 can continue to engage.This provides Operation to the clutch of torque-transmitting mechanisms B and D, therefore allows variator 12 to run by default.
With reference to Fig. 4 A- Fig. 4 B and Fig. 3 A- Fig. 3 B are referred again to, hydraulic control system 300 is changed by hydraulic control system 200 Get.Hydraulic control system 300 also include by increased often low (closing) electromagnetic valve 304 and by solenoid control subsystem 202 The solenoid control subsystem 302 that modification gets.Additionally, stop valve 306 be located at electromagnetic valve 304 and clutch control valve C4 it Between.Replace directly supplying clutch control valve C4 to main supply line 114, hydraulic line 308 is connected to main supply line 114, which is also connected to stop valve 306.Hydraulic oil is directed to clutch control from stop valve 306 by stop valve discharge pipe line 308 Valve C4.
During normal system operation, electromagnetic valve 304 is to cut out, and stop valve 306 is normally closed.In the default conditions phase Between, the open position of VFS electromagnetic valves 204 allows to continue operation to torque-transmitting mechanisms B.Back Up Source by using control power (not shown), electromagnetic valve 304 are opened, and this will open stop valve 306 to allow the hydraulic pressure in main supply line 114 to be led Cause clutch control valve C4, it is allowed to which torque-transmitting mechanisms D continues institute's selection operation, available so as to provide extra moment of torsion and gear Property.
Description of the invention is merely exemplary that the modification without deviating from general essence of the present invention is intended to locate in itself Within the scope of the present invention.Such modification has been not to be regarded as a departure from the spirit and scope of the invention.

Claims (10)

1. a kind of hydraulic control system for motor vehicles multi-mode electro-mechanical drive unit, including：
Multiple torque-transmitting mechanisms, each torque-transmitting mechanisms include at least one friction clutch；
Multiple clutch control valves, are in fluid communication with the torque-transmitting mechanisms respectively, and can when activateding Operate for the state of the torque-transmitting mechanisms to change over clutched state from clutch off-state；
Multiple electromagnetic valves, are matched and are in fluid communication with the clutch control valve respectively；And
Normally opened force-variable electromagnetic valve, is in fluid communication with the electromagnetic valve, and the operation of the force-variable electromagnetic valve is any for arranging Electromagnetic valve under open mode and its hydraulic pressure between the clutch control valve of pairing.
2. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 1, also includes containing There is the main supply line of hydraulic fluid, each connection when the clutch control valve activated in the torque-transmitting mechanisms Arrive the main supply line.
3. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 2, also includes pump, The hydraulic fluid in the pump operated main supply line with movement simultaneously pressurizes to which.
4. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 3, wherein described Pump is fixed displacement pump.
5. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 2, also includes group Close hydraulic pressure collector, wherein, each in the electromagnetic valve and the force-variable electromagnetic valve and the assembled hydraulic collection pipe fluid Connection, the operation of the force-variable electromagnetic valve are used for the hydraulic pressure for arranging the assembled hydraulic collection line pressure hydraulic fluid.
6. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 1, wherein, described Multiple torque-transmitting mechanisms include four torque-transmitting mechanisms for limiting drive mechanism for vehicle and limit the 5th of brake coupling Torque-transmitting mechanisms.
7. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 1, also includes becoming Fast device control module, the transmission control module are connected to and order each described electromagnetic valve and the force-variable electromagnetic valve Operation.
8. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 7, wherein, described Electromagnetic valve includes first, second, third, fourth and fifth electromagnetic valve, by the transmission control module and the pairing from It is identical that clutch control valve orders the first, second, third, fourth of opening or the 5th any one in electromagnetic valve to be all exposed to together Hydraulic fluid pressure under.
9. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 1, wherein described Multiple electromagnetic valves can make the off status and the one kind made in the open state of the electromagnetic valve opening of the closed electromagnetic valve respectively Operate under state.
10. the hydraulic control system for being used for motor vehicles multi-mode electro-mechanical drive unit as claimed in claim 1, wherein described In electromagnetic valve, predetermined several force-variable electromagnetic valves for being provided as providing under normally open, predetermined in the electromagnetic valve Several during the default conditions of the hydraulic control system of the operational control for losing the electromagnetic valve, it is allowed to be in fluid communication with Kept for two in the clutch control valve in the clutched state.
CN201610729192.9A 2015-09-08 2016-08-25 The hydraulic control system of multi-mode electro-mechanical drive unit for automatic transmission Expired - Fee Related CN106499814B (en)

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US14/847,456 US9856974B2 (en) 2015-09-08 2015-09-08 Hydraulic control system for a multiple mode electro-mechanical drive unit of an automatic transmission

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108626383A (en) * 2017-03-16 2018-10-09 通用汽车环球科技运作有限责任公司 Hydraulic control system for automatic transmission
CN111536167A (en) * 2019-02-07 2020-08-14 现代自动车株式会社 Clutch current control circuit and electric control valve with same

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10161508B2 (en) * 2015-05-05 2018-12-25 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having default gears applied through a clutch hydraulic exhaust circuit
DE112018003353T5 (en) 2017-06-30 2020-03-12 Allison Transmission, Inc. Control system and process therefor for a multi-speed transmission
US10576837B2 (en) * 2018-07-11 2020-03-03 GM Global Technology Operations LLC Electrical drive unit
US11181193B2 (en) 2019-11-27 2021-11-23 Allison Transmission, Inc. Power off hydraulic default strategy

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3844039A1 (en) * 1987-12-28 1989-07-13 Mazda Motor HYDRAULIC CONTROL FOR AUTOMATIC TRANSMISSION
US5063813A (en) * 1989-07-20 1991-11-12 General Motors Corporation Hydraulic control system for vehicular automatic transmission
US5417626A (en) * 1988-10-26 1995-05-23 Zahnradfabrik Friedrichshafen Ag Electronic-hydraulic control device for transmission systems of vehicles with automatic gear change
CN102230533A (en) * 2011-04-22 2011-11-02 安徽江淮汽车股份有限公司 Hydraulic control system for dual-clutch automatic transmission
CN102252088A (en) * 2009-12-10 2011-11-23 通用汽车环球科技运作有限责任公司 Control system for a dual clutch transmission
CN102563053A (en) * 2010-12-08 2012-07-11 通用汽车环球科技运作有限责任公司 Electro-hydraulic control system and method for a dual clutch transmission

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5931757A (en) 1998-06-24 1999-08-03 General Motors Corporation Two-mode, compound-split electro-mechanical vehicular transmission
US8904893B2 (en) * 2010-12-06 2014-12-09 Gm Global Technology Operations, Llc Method of controlling a dual clutch transmission
US8942901B2 (en) * 2010-12-09 2015-01-27 Gm Global Technology Operations, Llc Method of controlling a hydraulic control system for a dual clutch transmission
US8464851B2 (en) * 2011-04-04 2013-06-18 GM Global Technology Operations LLC Electro-hydraulic control system for an automatic transmission
US8783135B2 (en) 2012-08-09 2014-07-22 GM Global Technology Operations LLC Electro-mechanical drive-unit

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3844039A1 (en) * 1987-12-28 1989-07-13 Mazda Motor HYDRAULIC CONTROL FOR AUTOMATIC TRANSMISSION
US5417626A (en) * 1988-10-26 1995-05-23 Zahnradfabrik Friedrichshafen Ag Electronic-hydraulic control device for transmission systems of vehicles with automatic gear change
US5063813A (en) * 1989-07-20 1991-11-12 General Motors Corporation Hydraulic control system for vehicular automatic transmission
CN102252088A (en) * 2009-12-10 2011-11-23 通用汽车环球科技运作有限责任公司 Control system for a dual clutch transmission
CN102563053A (en) * 2010-12-08 2012-07-11 通用汽车环球科技运作有限责任公司 Electro-hydraulic control system and method for a dual clutch transmission
CN102230533A (en) * 2011-04-22 2011-11-02 安徽江淮汽车股份有限公司 Hydraulic control system for dual-clutch automatic transmission

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108626383A (en) * 2017-03-16 2018-10-09 通用汽车环球科技运作有限责任公司 Hydraulic control system for automatic transmission
CN111536167A (en) * 2019-02-07 2020-08-14 现代自动车株式会社 Clutch current control circuit and electric control valve with same
CN111536167B (en) * 2019-02-07 2023-05-16 现代自动车株式会社 Clutch current control circuit and electric control valve with same

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